Power transmission or clutch



.Dec. l2, 1939. vw. D. HUFF 2,183,454

POWER TRANSKISSION 0R CLUTCH Filed April 21, V1958 3 'Sheets-Sheet 2 Dec. 12, 1939. w. a Hur-'F POWER TRANSMISSION 0R CLUTCH Filed April 21, 1958 s sheets-sheet s Patented Dec. 12, 1939 UNITED STATES ATENTOFFICE William D. Huff, Lafayette, La.

Application April 211, 1938, SerialfNo.l 203,449y

11 Claim.

The present invention relates to-improvements in power transmissions and clutches, and relates generally to that class of device employing reciprocating pistons carried about in rotating cylinders from which fluid is excluded or to which it is admitted under restriction to couple the driver to the follower.

The purpose of the invention is to improve the mechanical operation of such devices to effect the general objections of smoother operation and more perfect balance whereby the device may more eiectively function .as a ily-wheel.

Another object of the invention is to introduce into the construction cams of peculiar formation so angularly set with respect toone another that they will balance the actions of the parts and move eiiciently to cut off and restrict the ow of the fluid to the cylinders and pistons.

A further object of the invention is to provide for; reciprocating cylinders in conjunction with abutments whereby the cylindersthemselves act to diminish the port area or to close the ports altogether when the driver is to be locked to complete engagement or direct drive with the follower member. l

A still further object of the invention is the simplification of the mechanical arrangement and its close grouping into a simply operating and efficient clutch and transmission unit which will provide smooth and continuous drive throughout all progressive phases of the 'drive ratios.

With the foregoing and other objectsin view, the invention will be more fully described hereinafter, and will 'be more particularly pointed out in the claims appended hereto.

In the drawings, `wherein like symbols Vrefer to like or corresponding parts throughout the several views:

Figure l is a front elevation,with parts broken away and parts shown insection,"of an improved power transmission and clutch constructed in accordance Vwith the present invention.

Figure 2 is a vertical central section taken on the line 2 2 in Figure 1 Figure 3 is affront elevation of the main cam showing its development.

Figurel is a plan View of the cylinder operating fork.

Figure 5 is a cross section rtaken on the line A5 5 in Figure 4. n

Figure 6 is a plan view of the kcontrol cam.

Figure '7 is anedge view of the same, `and.

Figure 8 is a fragmentary sectional view, taken on an enlarged scale, of the meeting portions of the cylinder and abutment, and showing a slight modification.

Referring more particularly to the drawings,

I designates a drum or Ya drum-shaped member which may be formed of aring casting, recessed and machined, as indicated at `2 and 2', for receiving and centering the margin portionsof the heads 3 and 3 which enclose the drumv and enable it to hold water, oil or other fluid customarily employed in transmissions of thisY character.

This drum is driven by the drive shaft 4, the drive shaft 4 having a iiange 5 bolted or screwed to the head 3 of the drum. The drum has a number of openings 6 distributed around its periphery. Four such openings `are shown in the drawings. These openings' are slightly larger in diameter than the outside diameter of the cylinders 8. Heads 'I are fitted to the openings and held in place by the vcap screws '9. Such' heads have inner reduced parts carrying Vpacking rings Ill. The rings I and the reduced parts of the heads 'form circular abutments to receivethereagainstthe beveled edges II ofthe reduced ring portions I2 of the cylinders 8.

'In other words'the beveled'edgel I I of the outwardly moving cylinder8 will iirst encounter the compression ring III and* compress said ring wherebythe reduced area I2 ofthe cylinder may lit tightly about said ring IIl whereby toexclude fluid from either entering orbeing expelled from the cylinder 8.

In this connection attention .is called more particularly to the enlarged view of the meeting portions of the cylinder and abutment as -shown in Figure 8. In this viewthe-.bevel yedge II` on the interior of cylinder 8 extends all the way `out to the external wall `of said cylinder and there is no external bevel on the cylinder as shown, for instance, in Figure 2. The external bevel on cylinder 8 of Figure 2 is without mechanical siglnii'lcance.

Figure 8 shows that the bevelfedge II is a leadingfedge moving in advance of the restricted area I2 which is a flat area. ,In Lother words.the area I2 is substantially parallel with .the interior and exterior walls of the cylinder 8. 'It 'is also substantially parallel with the yvertical wall of abutment 1 whereby the at restricted surface will mate with the flat vertical wall of abutment 'I in which the ring I0 is mounted. The restricted area I2 is of suflicient vertical extent .to span the groove in which the compressible compression ring I2 is mounted.

,Figure A8 also shows the interior area I I i which ist is also a bevel area. The area I Ia is, however, shorter in a direction cf the axis of cylinder 8 as compared with bevel area I I. In other words the area Il is shorter and more abrupt than the bevel area II which is longer and less sharp. Both areas II and I Ia slope inwardly of the inner Wall of cylinder 8 to the restricted flat surface I2. rIhese bevel areas combined with the restricted area I2 are designed to compensate or balance the pressure of fluid against cylinder 8 when being forced through the restricted area between the bevel portion I I and the rounded portion of head or abutment 1. v

The driven shaft or follower is shown at 4 and is centrally supported in the drum, as by the ball bearings I3 and I3. The ball bearings I3 are supported in a recess in the head 3. The ball bearings I3' are supported in a recess in head 3'. The driven shaft 4 carries the main driving cam I4 which may be made integral therewith or separately made and united xedly thereto. The driven shaft 4 has a reduced extension I5 lying beyond the cam I4. The reduced end 50 of the shaft extension I5 is journaled in the ball bearings I3'. Such extension I5 is machined to slidably receive thereon the cone cam I6. Axial sliding movement of the cam I6 is permitted along the key I1 but the cam is keyed to the driven shaft and is compelled by the key I1 to rotate therewith. The control cam I6, being on a machined extension I5 of the driven shaft 4' which carries the main cam I4, both such cams will be in proper alinement with one another.

The drum I also carries guides I8 which may be cast integral with the drum. These guides are of the same number as the cylinders, preferably four and they form mountings in which the cylinders 8 are free to slide in radial directions with respect to the axis of the drum and the axes of the drive and driven shafts are coincident. The guides I8 are also preferably alined with the openings 6 in order to hold the cylinders 8 in position whereby such cylinders will properly fit over the heads 1. The pistons are indicated at I9 and carry packing rings 20 in order to make a substantially fluid tight fit with the cylinder walls. The connecting rods for the pistons are shown at 2|, the same being bifurcated and carrying ball bearing rollers 22 bearing upon the periphery of the main cam I4. l l

Rocker arms 23 pivot about the pins 24 which connect the inner ends of such rocker arms with the inner ends of the connecting rods 2! and serve also as centers about which the rollers 22 rotate over the cam surface. The rocker arms operate in pairs, as shown in Figure l. The two arms 23 of each pair oscillate about a pin 25 affixed to the head 3'. The tail pieces of the rocker arms 23 are constantly forced apart by a coil spring 25' to hold the rollers 22 against the periphery of the driving cam I4.

As shown more particularly in Figure 2. push rods 26 are slidably mounted in brackets 5I affixed to the head 3'. At their inner ends the push rods carry canted or inclined ball bearing rollers 21 positioned in contact with the cone-shaped control cam I6. 'I'he inner ends of the push rods 26 are bent so that the surfaces of the rollers 21 are in alinement with the conical surface of the cam I6 to permit such cam I6 to be adjusted longitudinally or axially along the follower shaft extension I5.

Stops 28 on the push rods 26 engage parts of the brackets 5I in the inner positions of the push rods when the rollers 21 are not engaged 119011 the cam surface. The brackets 5I carry ball bearing rollers 29 in rolling contact with the push rods 26 for permitting of the free and easy reciprocating movement of the push rods 26 through the brackets 5I in accordance with the motion imparted thereto by the control cam I6. The push rods at their outer ends are pivoted to the actuating forks or cranks 3D, the pivots being shown at 3I. Springs 32 are arranged to urge the push rod stops against the brackets 5I and the rollers 21 against the surface of control cam I6. The actuating forks or levers 30 are pivoted at 52 to the head 3' and such levers are bifurcated to embrace the guides I8. The ends of each bifurcation are forked as shown at 33. The forks are slidable in grooves 53 of plugs 34. These plugs are carried by the sides of the cylinders 8 by means of bolts 35. 'Ihe bolts, as shown in Figure 1, are such as to permit the plugs to rotate on the bolts 35 during the oscillating movement of the levers 30. Plugs 34 slide up and down in slots 54 in the guides I8.

Referring to Figure 7, the control cam I6 is formed with a slot 36. As shown in Figure 2, a collar 31 is fitted in this slot whereby the cone cam I8 can rotate while the collar 31 remains relatively stationary; or whereby the collar 31 may rotate while the control cam I6 idles.

As shown in Figure 2, bolts 38 at their inner ends engage the collar 31 and pass slidably through the head 3' and the ange'. Suitable packing boxes 40 are mounted about the rods 38 at the flange 5. The outer ends of the bolts or rods 38 are attached to the flange of a collar 4I slidably mounted on the drive shaft 4. The collar is grooved to receive ring 42 loperatively connected with lever 43.

In operation, it will be seen that when the control cam I6 isdn the position shown in Figure 2 the largest diameter of this cam is in contact with the rollers 21 of push rods 25 and that consequently the cylinders y8 will be given the maximum movement of the actuated cranks 30, and moving outwardly from the center through the guides I8 will close the ports 44 of the cylinders 8 by bringing the reduced areas II and I2 in the outer edges of said cylinders 8 over the packing rings IIJ of heads 1. In this position, there being no escape for the fluid entrapped in the cylinders 8, the pressure on the pistons I9 is exerted ,through the connecting rods or links 2I, the ball bearing rollers 22 to the periphery of the driving cam I4, thereby causing the driven shaft 4' to rotate. In this position the mechanism acts as a clutch and the driven shaft 4 is caused to rotate at substantially the same number of revolutions asthe driving shaft 4. In other words the driver and follower are locked together in a direct drive.

Consider now the control cam :I6 as having been shifted by the shifting lever 43 to the other limit of its movement. In other words consider that the control cam I6 in Figure 2 has been moved over to its extreme left hand position. Then the small end of cam I8 does not contact the rollers 21 of push rods 26 and no movement will be exerted by cone cam I6 on the push rods. Therefore the springs 32 will hold the stops 28 against brackets 5I 'and there will be no movement of the cylinders 8, the cylinders remaining in their innermost position, leaving the port area 44 open to its maximum. The fluid in the drum will have free passage with the movement of pistons I9 without exerting any pressure on the driving cam I4. Therefore the driving shaft 'fi :willgcarrythedrum I around 'whilefthedriv'en A:shaft t'fremains stationary, p

' .Considerinowan intermediate position .offthe vconeuor...controlgcam I5. In. suchposition'ithe p'nsloirods '26 will'be given ia reducedthrow,z.and l fluidfor transmission and clutch purposes lbelthe ".cylindersfwill consequently have a' recipe `rocating;movement .in'radial .directions but of restricted `scope whereby `the :port area?v 44 will only y bereducedzat.eachipressurefstroke oitthe pistons 10 to thez'restrictionrequired to exertsuiiicient pressure against the driving carn I'43to lcause `the driven shaftn45t0 f'revolve .at any'speed-desired.r

20 "A suitablepacking lglandvlll .is .provided between' .drivenshafwl and vthe head-3. Thefpacking "glands 40 and 4l will 'retainthe fluid in .the

--drum when stationary and not in use. Whenin operation, vcerltriiugal force willl cause the iiuid to e, .25.press againstithe outer yportion of the drum and there will .be anv open space in the center around the/shafts 4 `and A4'. Ifthe heads 1 andthe plugs 46 areV made tight there will be no way'for fluid to escape and=the operation may continue-indefinitely withoutthe addition offurther luid.

At each inward movement of the pistons I9. f

the `cylinders 8 controlled by the cone cam I S will'leave the full open .area at 44. Under cen'- triiugal force the fluid in drum I will ll the cylinders and'pressj-againstthe .heads of the pis-` tons IB. At each outward stroke of the pistons, kthe area 44 will be reduced or restricted to form Suicient pressure 'against the piston to rotatethe driven shaft .4.

A40 The vworking cam I4 is a progressive cam as shown in Figure 3; .The shape of this cam makes -possible,.rst,'fthe outward movement of .two of the four pistons .before the othertwol pistons, start inward, thus, crossing centers as it were y 45 maintaining a constant pressurel from :the drive to the driven member. f

It also maintains a constant pressure at any position yon the progressive or driving-side of the .cam between` the'drive and the driven members.

y Also, the movement ofthe pistons from this cam is diametrically in opposite directions tol and from the'center which maintains a constant balance of all the moving parts permitting the device to be used as a balance wheelfor the driving iorce.

The cone-shaped ,cam It operates in synchro'- nized positionwith the above drivingor working cam if! and controls and regulates the closing v.and opening of the ports at'the outer ends of l the cylinders. `The `cone-shaped cam- I6 operates in synchronized position with the above working cam but has a lead in advance 'of working cam. f i y It will be noted that the outer portions lof the y 165 cylinders are `substantially non-restricted. There is a full area opening in the cylinders while the same are beingffilled. e

The cylinders are not filled by vacuum but by centrifugal force exerted on the fluid within the ,'70 drum. Thus, the faster the drum turns or revolves, the greater the force applied to fill the cylinders, and under this centrifugal force nothing but fluid is permitted to enter theA cylinders asall lighter fractions,r ysuch Aas air and rgases Aare driven inwardly,the heavier particles being thrown outwardly, :consequently the m'assLof-ithe `,iiuid entering the cylindersis dense .as compared 4withfiuid not operated uponfby 'centrifugal' force. IThis :dense'mass of :ud is substantially non- '.compres'si-ble :whichis a desirable condition inr cause of the fact that it avoids variation in the 4speed between .the drive and'the driven members. UThis rcondition :will also eliminateany possibility of .heat from compression, H10 Under centrifugaliorce there will be a greater pressurelexei'ted on the outer .surface of piston .headthan by the uid on the inner surface, thus 'notonlyrbalancing the weight ofthe piston but .also havingfa tendeneyto press the pistons `in:.15.

wardl-y and their rollers 22 againsty theperiphery `of working cam I4, reducing thework performed bythe coil springsZ. l

`All of thefvitalmoving parts are mounted on ball .bearings which ...are practical tooperate with;v 20 ywater lubrication, although @oilmay be the fluid `rmedium :or a mixture of oil andwater may be used..

-Adverting tothe stops 28 on push rods 26, when these stops are moved radially inward Vbyf25 the springs 321130 theextent that; they engage brackets 51,.' further inward radial `movement of Vpush rods "26' and rollers 21 :will cease. In other words, the stops suspend the 'movementy of the l.push rods when the cylinders -Bhave attainedo y Vtheir vmaximum opening. When the-cam lis positioned so that the smaller endof the lcam I6 is-not zincontact with'push rod rollers2'l,.the rollers LEaresuspended bythe stops 28 against the brackets .5I and need :not contact. the cam at'5135 lvall'in this position. .It :will be seen, when-in this position,- .the area 44 is opened to the' fullest extent andrremains so.

While the cone-shaped camlii `operates in convs'tantfpositionwith drive cam I4; this cam I6 is @V40 -so set with relation to cam I4 so as to move the Ycylinders before the pistons i9 are vactuated 'by cam-I4; By reference to Figure 6, and thelines shown thereon, :the lead ofthe `cam i6 is shown, the lead being .the circumferential area on cam 45 .16 by which the action of this cam precedes the actionyof theworking cam I4.

'Cam...l6 .is a conic sectionviewe'd axially as in Fig.j7. Viewed circumferentia'lly as in Fig. `6 :the cam/ has rhigh and low points 'rlaand `IIS" 50 respectively. The lines ISC .bounding the high and lowVV .points areshown in 4Iig "7at0 be vstruck -along lines .that converge toward fthe small end of the conic cam; this in'order that the` arcs vof fthe low points Ib shall ldiminish in ylength from .55 thelarger end of the coniccam to the smaller end thereof fin proportion to the diminishing .lengths of the high .points Ita. In other words as the diameter of the conic'cam changes from one end of the camto the other, the arcuate lengths i60 vof the high and llow points' tta and Itb must vary in proportion.

`In Fig. 2, the'rollers 2l rest upon the low points i6 of the cam at the endll of the conic cam having the greatest diameter. On rotation 'of shaft :'65

`4 the rollersjfl will ride :up on thev high points ISa, l thus pushing out arinsll' and cylinders' 'toa maximum. outerk position of the cylinders 8 where the ports 4,4 are completely closed. The lead of cam I6 over cam I4 will cause rclosing of cylinder l'70 ports -44 before the pistonsl start outward in the cylinders 8. But iffthe ports 44 are completely closed and` the cylinders previouslyflled with non-compressible iiuidf'from ywhich air and the like =are removed bythecentrii-ugal action,-then S75 the pistons I9 cannot'move outin cylinders 8 except there be leakage between the movable parts and the rollers 22 at the ends of the connecting rods 2| react on the surface of cam I4 to carry "5 cam and follower shaft 4 around with drive shaft 4. The shafts 4 and 4 are thus locked to rotate at substantially the same speeds together. Consequently the rollers 21 controlling the cylinders S of the two opposed pistons I9 exerting 10 pressure between the heads 1 and the periphery of cam I4 remain on the high points I6a of cone cam I6 and direct drive between the driver shaft 4 and the follower or driven shaft 4' is obtained when in this position. The rollers 21 controlling the i5 cylinders 8 of the other two opposed pistons I 9 are opposite the low points ISb and cam I6 and the springs 32 hold the rollers 21 against the low points |61) and the ports 44 of these two opposed pistons are open and these cylinders, under centrifugal force of fluid rotating in drum are being filled with fluid. Thus it will be seen that if account of leakage by packing rings 20 in pistons I9 or by the packing rings I0 in heads 1, the two opposed pressure bearing pistons IS should move 25 outward to the extreme of high points on cam I4,

the other two opposed pistons will have reached the low points of cam I4 thus filling these cylinders to capacity and the cam I6, revolving with cam I4, will have closed the ports 44 and because of the advance or lead of cam I6 over cam I4 and the design of cam I4, these pistons will have assumed the load before the first two pistons have released it. Thus while there may be a variation of naught to one or more turns per minute between the driving shaft 4 and the driven shaft 4',

there will be a constant pressure exerted between these shafts, one pair of opposed pistons taking up the load before the other opposed pair of pistons have released it.

When cam I6 is shifted to an intermediate position along the shaft 4 so that the high points IIa of the cam at this part of its conic section are not high enough to move cylinders 8 all the way out to meet heads 1, then the ports 44 will 45 not be fully closed; and, when the cam I4 follows the action of cam I6 the pistons I9 maymove outward in the cylinders 8 at a rate of speed dependent on the size of port area 44. This will allow a certain slippage of rollers 22 on cam I4 and hence a lag of follower shaft 4 behind the speed of drive shaft 4. The further cam IB is adjusted to the left in Fig. 2, the wider will be the openings of ports 44 and the less speed transmitted to follower shaft 4'.

55 In any position of cam I 6 except at the extreme left and the complete disengagement of follower or driven shaft 4 from the driver shaft 4 and where the follower shaft 4 lags behind the drive shaft 4 there will be relative rotation of cam I6 with respect to rollers 21; thus causing rollers 21 to ride in and out on the high and low points I6a and Ib, This will result in the radial reciprocation of cylinders 8 as the drum rotates. The pistons I9 carried around in the cylinders 8 will reciprocate radially in the cylinders 8 due to the relative movement of the rollers 22 over the surface of cam I4. lDue to lead of cam I6 over cam i4 the cylinders 8 will be moved out to the position of selected port area before the pistons I9 start on their outward movement. Consequently the transmission reduction in speed of the follower shaft 4' is that selected by the axial position of cam I6 along the extension I5 of follower shaft 4. The low points Ib allow cylinders 8 to be drawn in, thus exposingwide port areas 44 at the time' pistons I9 are moving inwardly, whereby to avoid formation of vacuum whichv would tend to hold pistons 'I9 in the outer positions and draw rollers 22 off surface of cam I4. Thev reengagement of the rollers 22 with cam 5 surface I4 would were this latter condition to obtain no doubt be attended with noise and clutch chattering and possible damage to the parts. Any pulsating movement which might take effect'in the follower shaft 4' due to this re- 10 ciprocation of the cylinders 8 and the pistons I9 is offset by the plurality of cylinders and pistons, which work in diametric pairs.

It will be noted that due to lead of cam I 6. cylinders 8 are moved radially in to thus unre 15 strictedly open ports 44 to completely relieve vacuum from pistons I9 when they begin to move radially inward.

The invention makes practical use of the law of centrifugal force for the purpose of lling thefL20 cylinders with de-aerated liquid whereby to create greater clutch ei'iciency.

It is obvious that various changes and modiiications may be made in the details of construction and design of the above specically described? `25 embodiment of this invention without departing from the spirit thereof, such changes and modiiications being restricted only by the scope of the following claims.

What is claimed is: i

1. In an improved power transmission and clutch, drive and driven members, a drum for containing fluid xed to one member, abutments on the drum, cylinders carried around with the drum and movable relatively to the drum toward 35 and from said abutments, pistons mounted to reciprocate in said cylinders, cam connections between said pistons and the other member, and means for causing the automatic reciprocation of the cylinders toward and from the abutments 40 concurrently with the rotation of the drum, said means including means for controlling the throw of movement of said cylinders relatively to said abutments and also including means to suspend the reciprocating movement of the cylinders when "45 said first-named means is positioned to disconnect the driven member from the drive member.

2. In an p improved power transmission and clutch, drive and driven members, a drum for containing fluid xed to rotate with one mem- Y50 ber, abutments on the drum, cylinders carried around with the drum and movable relatively to the drum toward and from said abutments, said cylinders having open ends closed or restricted in port area by said abutments, pistons mounted to l'55 reciprocate in said cylinders, cam connections between said pistons and the other membernneans connected between said cylinders and members for reciprocating the cylinders toward and from said abutments automatically as the drum rotates '60 whenever a diierential in speed occurs between the drive and driven members, said means including means for varying the degree of the reciprocating movement of said cylinders to control the port area at the abutments, said means 65 timed with respect to the movement of the pistons whereby the cylinders will be moved away from the abutments relieving the restriction to the lling of the cylinders during the inward strokes of said pistons, said first-named means including 70 means for holding the cylinders without reciprocation substantially a maximum distance from said abutments when the first-named means is positioned to disconnect the driven from the drive member whereby'the pistons will be free to re- 75 clutch, drive andjdrven members, a -drum xed ciprocate in said i cylinders@ without impedance from any fluid trapped in saidcylinders.;

. 3. In.l an improved power` .transmission andl clutch, drive.v andr driven members, a drum containing fluid fixed to rotate with one member, a

cam fixed to rotate with lthe other member, cylinders` carried around with said drum and havingv a reciprocating` movement with respect to the drum, said cylinders being open at their outer ends, abutmentscarried yby the drum toward which the outer open ends of said cylinders are adapted to move, pistons reciprocating in said cylinders, rollers connected to said pistons and bearing on the periphery of said cam, means for urging the rollers against the cam surface, and means for reciprocating said cylinders, said last named means including means for Varying the reciprocating throw of said. cylinders.

4. In an improved power transmission andi clutch, drive and driven members, a, drum for uid connected flXedly to one member, a cam fixed to the other member, lcylinders carried about with said drum and having a reciprocating movement relatively to the drum, said cylinders having outer open portions, abutments on the drum toward which the outer open portions Aof said cylinders are adapted to move, pistons mounted to reciprocate in said cylinders, rollers yieldably urged against said cam and connected to the pistons, and means to reciprocate said cylinders, said means including a slidable cone cam with means to slide the cam to vary the throw of said cylinders.

5. In an improved power transmission and clutch, drive and driven members, a drum for iiuid connected to one member, a cam xed to the other member, cylinders rotatable with said drum and reciprocating with respect to the drum,l

said cylinders having open outer ends, abutments for receiving the open outer ends of the cylinders when in theirV outermost positions, pistons reciprocating in said cylinders, rollers e yieldably urged against the cam and connected to said pistons,'and means to reciprocate said cylinders, said means including a cone cam slidably mounted to vary the throw of said cylinders, said cone cam having circumferentially elongated high points and minor low points, said rst mentioned cam having major W points and circumferentially minor high points, thehigh and low points of the two cams being so angularly set that the Cylinders will be rapidly shifted to outer position prior to outer movement of the respective pistons.

6. In an improved power transmission and clutch, drive and driven members, a drum containing iuid carried around with one of said members, a cam xed to the other member, cylinders carried about by said drum and reciprocating with respect to the drum, said cylinders having ports, the movement of said cylinders adapted to open and close said ports, means for reciprocating said cylinders including a cam struck on a conic section, push rods movably mounted in the drum and bearing on the surface of said conic cam, means for shifting the conio surface of said cam with reference to said push rods to vary the throw of the push'rods, levers connected to said push rods and to said cylinders, pistons in said cylinders, and means connected to said pistons and bearing on the surface of the first mentioned cam and moved thereby on differential circumferential motion between said members.

7, In an improved power transmission and to movefwithone member, and; containing` fluid, cylindersA carried around with; said` drum and having reeiprocatingmovement with respect to said drum-, saidy cylinders having ports openedand closed bythe reciprocatingV movement thereof, means` yfor reciprocatingr lsaid cylinders including reciprocating push rods, guide brackets `on the drum for guiding themovements of said push rods,v said brackets and push rods having stop means therebetween tolimit theinward motion of said lpush rods, spring means acting; on said push .lfQdsto Ayieldably move.: the Same. inwardly,

levers pivoted to said push rods and to said drum and connected to move said cylinders, a movably mounted cone cam engaged by the inner portions of said push rods, means for shifting said cam, pistons inr said cylinders, a working cam on the driven member, and means yieldably pressed against the surface of said working cam and connected to said pistons.

8. In an improved pofwer transmission and] clutch, drive and driven members, a drum secured to move with one of said members, a working cam secured to move with the other member, an extension on the driven member beyond said working cam, a cone control cam secured to rotate with the driven member and slidable axially on said extension, means to shift said control cam, reciprocating cylinders carried about with said drum, means moved by said control cam for reciprocating said cylinders, pistons in said cylinders, means connected to said pistons and bearing on saidy working cam, said cylinders having ports opened and closed by the reciprocation thereof.

9. In an improved power transmission and clutch, drive and driven members, a fluid drum iixed to move with one of said members, bearings in said drum for receiving an end portion of the driven member, a working cam in said drum xed to the driven member, a control conic cam in the drum xed to rotate with said driven member but slidable thereon and moving concentric with said working cam, means extending to the exterior of the drum for causing axial shifting movement of said conic cam, cylinders carried about with said drum and reciprocating in said drum, means for reciprocating said cylinders acted on by said control cam, pistons movably mounted in said cylinders, and means connected to the pistons bearing yieldably against the surface of said working cam.

10. In an improved power transmission and clutch, drive and driven members, a uid drum moving with one of the members, bearings in the drum for receiving an end portion of the other member, a working cam fixed on the driven member, a control cone cam sliding on the driven member kbut xed to rotate therewith, guides xed in the drum, cylinders mounted to reciprocate radially in said guides, levers pivoted in the drum having forked parts for reciprocating sa1d cylinders, means projecting from the cylinders slidably engaged by said forks, connections between said levers and the conic cam, pistons movably mounted in said cylinders, and means connected to the pistons for yieldingly bearing against said working cam, said cylinders having ports opened and closed by the reciprocating movement thereof. f

11. In an improved power transmission and clutch, drive and driven members, a uid drum connected to one member, a Working cam fixed to the other member, a com'c control cam driven by IVO two diametric pistons before the other two pistons at right angles thereto start inward thus maintaining a constant pressure from the drive to the driven member and also maintaining a constant pressure at any position on the progressive or driving side of the working cam between the drive and the driven member, said cone control cam occupying a synchronized position with said working cam and having a lead corresponding with but in advance of the lead on the work- 10 ing Cam,

WILLIAM D. HUFF.

Lear

luf-s 

